EP1908972B1 - Decoupling device for mounting a support shaft on a base and radial ondular washer - Google Patents

Abstract

Decoupling device for mounting a shaft, especially a shaft of a spherical-disk-shaped enveloping gear operating with a chain as the enveloping device, on a base body (8) has an outer bearing ring (4) having a circular cylindrical outer surface (14) and inside which the shaft is mounted, and an inner surface (16) surrounding the outer surface and rigidly connected to the base body. At least one radial ondular washer (18a) arranged between the outer surface and the inner surface allows restricted relative radial movement between the inner surface and the outer surface under elastic deformation. Independent claims are also included for radial ondular washers.

Description

The invention relates to a decoupling device for a bearing of a shaft on a base body, in particular a shaft of a chain with a belt as a belt CVT. The invention further relates to a radial wave spring for such a decoupling device.

Recently, increasingly used in motor vehicles conical-Umschlingungsgetriebe with continuously variable translation use. Such belt pulleys comprise two pairs of conical pulleys mounted on shafts spaced apart from each other, which are looped around by a belt which is frictionally engaged with the conical surfaces of the pulley pairs. By opposing change in the distance between the conical disk pairs, the ratio of the transmission can be changed continuously. As a belt, in particular in transmissions, with which higher torques can be transmitted, for example, torques in the range of 300 Nm and more, metallic chains used.

From the German patent application DE 102 03 307 A1 a bearing arrangement for such a conical-pulley transmission is known. A bearing assembly for supporting rotatable shafts of the transmission is described, which comprises a bearing with a bearing outer ring and a bearing inner ring, wherein the bearing outer ring is axially secured in a receptacle on side surfaces of the receptacle and the receptacle has a substantially cylindrical inner wall, wherein between the Bearing outer ring and the inner wall of the receptacle is arranged in the radial direction a flexible element. The flexible element consists of at least one corrugated in the radial direction or provided with projections ring element. Furthermore, flexible elements for vibration damping are provided in the axial direction.

An elastic element for tolerance compensating installation of bearings is in the Laid-open application DE 33 38 507 A1 disclosed. This elastic element is cup-shaped, wherein the jacket of a Fedemapfes consists of an arbitrary number of slats and are provided on the slats inwardly or outwardly directed hump. The element can also be formed from a closed shell with inwardly or outwardly exposed spring tongues. The fins or the jacket are formed on the side facing away from the bottom flange.

The invention has for its object to reduce the noise transmission, in particular the structure-borne sound transmission of the conical disks in a vehicle.

This object is achieved with a decoupling device for a bearing of a shaft on a base body, in particular a shaft of a chain belt as a belt-forming conical-pulley with the features of claim 1.

In the following advantageous embodiments and developments of the decoupling device according to the invention are exemplified, these examples are not exhaustive.

On the outer surface and radially extending to this side surfaces forming a radial spring spring spring sleeve is placed with a total U-shaped cross-section, the total axially parallel extending bottom is bulged radially.

The bottom of the spring sleeve has at least two axially spaced, circumferential radial corrugations with axial wavelength direction.

An annular region between the radial corrugations protrudes into a circumferential recess of the outer surface.

The bottom of the spring sleeve has at least one radial corrugation with a direction of wavelength extending in the circumferential direction.

Radial corrugations of the bottom with axial and / or circumferentially extending wavelength direction have different heights.

Radial side surfaces of the outer surface are based on radial side surfaces of the inner surface over the total radially extending, curved side walls of the spring sleeve in the axial direction elastically yielding each other.

The radial side walls of the spring sleeve are supported radially on an annular step of radial side walls of the outer surface and the voltage applied to the inner surface bottom of the spring sleeve is formed crowned.

The spring sleeve is formed with the bottom wall by cutting radial slots.

A circumferential projection of the bottom engages in an annular groove of the inner surface.

On at least one of the inner surface axially delimiting, radially inwardly extending side surface is formed an annular surface on which the spring sleeve is axially supported.

The side walls of the spring sleeve are axially and / or radially elastically yielding.

The radial wave spring is formed by extending over parts of the circumference of the inner surface and the outer surface extending spring segments.

The at least one radial wave spring is arranged on a radially loaded side of the bearing and extends over only part of the circumference and a positioning device is provided which determines the positioning of the at least one radial wave spring in the circumferential direction.

In the following examples of advantageous embodiments of the invention Radialwellfedem be called, which can be used in the decoupling device according to the invention.

A radial wave spring for enclosing at least a partial circumference of a bearing ring formed with a circular cylindrical outer surface and adjoining radial side surfaces is considered to be at least one circumferential segment the bearing ring enclosing spring sleeve formed with a total of U-shaped cross section, wherein at least the bottom of the spring sleeve has a resiliently deformable curvature.

The bottom of the aforementioned radial wave spring is formed with a circumferential radial projection.

The decoupling device according to the invention and the radial corrugated spring (s) according to the invention can be used for any types of bearing arrangements. Advantageously, they are used for rolling bearings, with such bearings, for example, the shafts of a conical-pulley belt are mounted.

The invention is explained below with reference to schematic drawings, for example, and with further details.

• Figuren 1, 3, 5, 7, 13, 18, 20, 22, 26, 28, 30, 34, 36, 38, 40, 42, 44 und 45 Teilschnitt-Ansichten von Lagerungen, geschnitten parallel zur Lagerachse;
• Figuren 2, 4, 6, 8, 14, 15, 16, 27, 29, 37, 39 und 43 Teilschnitt-Ansichten der verschiedenen Ausführungsformen von Lagerungen, geschnitten senkrecht zur Lagerachse;
• Figuren 9 und 11 Teilseiten-Ansichten zweier verschiedener Ausführungsformen von Radialwellfedern;
• Figuren 10 und 12 Ausschnitte der Ansichten der Figuren 9 und 11;
• Figur 17 einen Teil-Aufsicht, teilweise geschnitten, einer Lagerung mit einer besonderen Ausführungsform von Radialwellfedern;
• Figuren 19 und 21 Teil-Seitenansichten von Radialwellfedern;
• Figuren 23 einen vergrößerten Ausschnitt der Figur 22;
• Figur 24 eine Teil-Seitenansicht einer Radialwellfeder;
• Figur 25 eine Teil-Aufsicht auf nebeneinander angeordnete Radialwellfedern;
• Figur 31 einen vergrößerten Ausschnitt der Figur 30;
• Figur 32 eine Teil-Seitenansicht auf eine Radialwellfeder;
• Figur 33 eine Teil-Aufsicht auf nebeneinander angeordnete Radialwellfedern,
• Figur 35 einen Ausschnitt der Figur 34;
• Figur 41 einen vergrößerten Ausschnitt der Fig. 40,
• Figuren 46 und 47 Teilschnitt- und Teilseiten-Ansichten zweier weiterer Ausführungsformen von Radialwellfedern,
• Figuren 48 und 49 Perspektiv-Ansichten zweier verschiedener Anordnungen von Radialwellfeder-Segmenten mit Positionier-Bauteilen;
• Figur 50 eine Seitenansicht eines Radialwellfeder-Segments, wie es in den Figuren 48 und 49 verwendet wird;

They show:

• Figures 1, 3, 5 . 7 . 13 . 18, 20 . 22 . 26, 28 . 30 . 34 . 36 . 38 . 40 . 42, 44 and 45 Partial sectional views of bearings, cut parallel to the bearing axis;
• FIGS. 2, 4, 6 . 8th . 14, 15, 16 . 27, 29 . 37 . 39 and 43 Partial sectional views of the various embodiments of bearings, cut perpendicular to the bearing axis;
• FIGS. 9 and 11 Partial side views of two different embodiments of radial wave springs;
• FIGS. 10 and 12 Excerpts of the views of the FIGS. 9 and 11 ;
• FIG. 17 a partial plan view, partially in section, a storage with a particular embodiment of radial wave springs;
• FIGS. 19 and 21 Partial side views of radial wave springs;
• Figures 23 an enlarged section of the FIG. 22 ;
• FIG. 24 a partial side view of a radial wave spring;
• FIG. 25 a partial view of juxtaposed radial wave springs;
• FIG. 31 an enlarged section of the FIG. 30 ;
• FIG. 32 a partial side view of a radial wave spring;
• FIG. 33 a partial view of juxtaposed radial wave springs,
• FIG. 35 a section of the FIG. 34 ;
• FIG. 41 an enlarged section of the Fig. 40 .
• FIGS. 46 and 47 Partial sectional and partial side views of two further embodiments of radial wave springs,
• Figures 48 and 49 Perspective views of two different arrangements of radial wave spring segments with positioning components;
• FIG. 50 a side view of a radial wave spring segment, as in the Figures 48 and 49 is used;

According to FIG. 1 a shaft, not shown, of a cone pulley pair of a conical-pulley belt drive is enclosed by a bearing inner ring 2, rolling elements 6 are arranged between it and a bearing outer ring 4 arranged concentrically therewith so that the components 2, 4 and 6 together form a roller bearing. It is understood that the outer surface of the bearing inner ring 2, on which the rolling elements 6 roll off, can be formed directly by a correspondingly machined outer surface of the shaft, not shown. The bearing outer ring 4 is received in an annular recess of a base body 8, for example a gear housing, according to FIG. 1 is closed to the right by a removable ring cover 10.

The outer surface of the bearing outer ring 4 is not supported directly at the bottom of the annular recess, but with interposition of different More specifically, in the example shown between the outer surface 14 of the bearing outer ring 4 and the inner surface 16 of the shell 12 four annular radial corrugated springs 18a are arranged between which stop rings 20a are arranged for axial distance assurance. On both sides axially outside spacer rings 22a are provided.

The stiffness of the radial shaft springs is such that the desired stiffness of the bearing with respect to radial displacements of the bearing shaft, not shown, is achieved with the four radial wave spring rings or radial corrugated springs. While the radial wave springs 18a, as out FIG. 2 which is a detail view of the FIG. 1 in the direction AA, are shaped so that they are constantly in contact with the outer surface 14 and inner surface 16, the stop rings 20 are dimensioned such that there is a radial clearance d between them and the housing ring 12. In this way, the bearing outer ring 4 according to FIG. 2 move under elastic deformation of the radial wave springs 18a by a distance d up until the stop rings 20 come into contact with the inner surface 16.

The housing ring 12 made of steel, for example, is optional and serves, for example, to prevent wear of the recess or bore of the base body 8, which may consist of light metal.

In the following embodiments, based on the Figures 1 and 2 are explained in similar views, only those components are provided with reference numerals, which are essential for explanation.

While in the embodiment according to the Figures 1 and 2 the radial wave springs 18a have substantially constant cross-section along the circumference and are corrugated only in the circumferential direction are in accordance with the embodiment FIGS. 3 and 4 the radial corrugated springs 18 b provided with bumps and are provided between the radial corrugated springs 18 b and axially outside only positioning rings 22.

How out FIG. 4 As can be seen, the radial wave springs 18a are provided inwardly and outwardly with circumferentially spaced support bumps 24 which are in constant abutment against the outer surface 14 and inner surface 16, respectively. Between the Auflagerhöckern 24 bumps 26 are formed between which and the respective surfaces in the unloaded state of the bearing outwardly a game e and inwardly there is a game f. As shown, the abutment bumps 26 are preferably each on the opposite side of the support cusps 24 of the radial wave springs 18b. At a certain deformation of the radial wave springs 18b, the abutment bumps 26 act as stops, so that under high load both the support and the stop bumps support points for supporting the bearing outer ring 4 on the base body 8, resulting in a uniform support of the bearing.

The FIGS. 5 and 6 show a den FIGS. 3 and 4 largely corresponding training of storage or decoupling of the bearing outer ring 4 from the main body 8, by means of the noise transmission from the rolling bearing is reduced in the body. In the embodiment according to FIGS. 5 and 6 are the stop bumps 26 of different heights. It is assumed that the bearing is loaded vertically upward in the direction of the arrow S or radially displaced. In games of the same length e and f, the play f at the apex S is completely used up, whereas a residual clearance remains between the adjacent bumps and the associated surfaces, since the approach to these points is smaller in accordance with the circumferential angle φ.

• x(ϕ) = x_max • cos (ϕ), wobei x_max das Spiel am Scheitelpunkt ist.

So that the attacks come simultaneously to the effect, the radial games are adapted to the individual humps according to the respective angular position. This leads to a more even load distribution for the bearing. For the individual games:

• x (φ) = x _max • cos (φ), where x _{max is} the game at the vertex.

It is advantageous in many respects to fix the radial wave springs or spring rings in the circumferential direction. The positioning of the radial wave springs in the circumferential direction can be done in different ways.

According to FIGS. 7 and 8 engages a pin 28 which engages in a recess 30 of the housing ring 12, in addition to a slot 32, with which the radial wave springs 18 are formed. As can be seen immediately, the pin 28 is held in this way in the circumferential direction immovably between the bearing outer ring 4 and the housing ring 12 so that it fixes the or the radial corrugated springs 18 in the circumferential direction.

It is advantageous if the waves or bumps of adjacent radial corrugated springs are offset in the circumferential direction to each other in order to achieve the most uniform loading of the bearing. In order to realize a mutual offset of the circumferentially fixed radial wave springs, different radial wave springs would have to be manufactured with different relative arrangement of slot and bumps or waves. To reduce the variety of variants, it is advantageous to place the slot 32 between bumps such that when alternately reversed, that is rotated by 180 ° mounting the radial corrugated springs, the desired positioning is achieved.

It is advantageous to attach the slot 32 centrally between a radially outer support bump 24 and a radially inner support bump 24, as in FIGS. 9 and 10 shown, where Fig. 10 an enlarged section of the Fig. 9 shows.

How out Fig. 10 immediately visible, is located at the continuously drawn radial wave spring 18b left of the pin 28, a radially outward bearing cradle and right of the pin 28 a radially inwardly directed support hump. Further, to the left of the pin is a support hump 24 opposite, radially inwardly directed abutment bump and right of pin 28 a support cusp 24 opposite, radially outwardly directed abutment bump 26. In 180 ° twisted installation of the radial wave spring 18b results in the dashed line arrangement, that is a stop bump is a support cusp axially adjacent.

It is understood that there are numerous other possibilities of cusp or shaft arrangements and slots, with which results in the smallest possible component diversity with respect to the radial wave spring as uniform as possible power distribution.

Because of the small differences in the Höckerhöhen it is difficult in accordance with training of the radial wave springs FIGS. 9 and 10 their correct, that is each rotated by 180 ° installation recognized. This problem can be solved by that according to FIGS. 11 and 12 the slot 32 is formed with side walls 34 which are inclined to the radial direction. This can be detected in a simple manner, whether axially adjacent radial corrugated springs are installed rotated by 180 °.

For the circumferential fixation of the radial wave springs 18 relative to the base body 8, there are a wide variety of possibilities. FIGS. 13 and 14 show a feather key 36 which is inserted into a groove in the base body 8 and penetrates slots in the housing ring 12 and the radial field spring 18.

FIG. 15 shows an embodiment in which the housing ring 12 is provided with a radial rib which engages in the slot 32 of the radial wave spring 18.

In the embodiment according to FIG. 16 the radial wave spring 18 is provided with a radially outwardly extending rib 40 which engages in a recess of the housing ring 12. The housing ring 12 is held immovably in the circumferential direction on the base body 8.

Another arrangement for the axial fixing of the radial wave springs is in FIG. 17 shown. In this embodiment, each radial wave spring 18 c ends on one side of the slot 32 in an axially extending projection or pin 42. The pin 42 of the axially outermost radial wave spring engages in a recess 44 formed in a radial surface of the base body 8. The pins 42 of the axially adjacent respective radial corrugated springs engage in the slot 32 in accordance with FIG. 17 each right side adjacent radial wave spring. The radial wave spring rings can be inexpensively manufactured as stamped and bent parts.

Based on FIGS. 18 to 25 Be explained in the following further advantageous embodiments of devices with which the storage of the main body can be decoupled.

According to FIG. 18 the outer surface of the bearing outer ring 4 is provided with a wide circumferential groove 46, are arranged in the radial wave springs 18b. Radial Wave Springs For example, 18b may be similarly pre-assembled as retaining rings are mounted in shaft grooves. The remaining axially outside of the circumferential groove 46 shoulders of the bearing outer ring 4 (enlarged view X) can directly form a radial stop. Further, between side walls of the base body 8 and the ring cover 10 and the bearing outer ring O-rings 48 may be mounted for axial guidance.

The embodiment according to FIGS. 20 and 21 is different from that of FIGS. 18 and 19 merely in that in the outer surface of the bearing outer ring 4 a plurality of grooves 46 are formed, in each of which a single radial wave spring 18b is arranged.

In the embodiment according to FIGS. 22 to 25 the bearing outer ring 4 is provided with two circumferential grooves 46, wherein in accordance with FIG. 22 left circumferential groove three radial wave springs 18c are arranged and in the axially open right circumferential groove 46 four radial corrugated springs 18c are arranged. The formed on the base body 8 opposite or inner surface 16 has a step 50 on which the left Axialwellfeder is supported. The axially outermost radial wave spring 18 c in the right circumferential groove 46 is supported on a radially extending side surface 52 of the annular cover 10. FIG. 23 shows the section X of the FIG. 22 in an enlarged view. The individual radial corrugated springs 18c are similar in terms of their radial extent with bumps, for example, according to embodiment FIG. 4 trained (see FIG. 24 ). In addition, the radial wave springs 18c are corrugated in the axial direction, as shown FIG. 25 apparent, the one Top view of a portion of the axially adjacent radial wave springs 18c shows. With the arrangement according to FIGS. 22 to 25 a decoupling or acoustic decoupling of the bearing is achieved by the body in the radial and axial directions. The formed between the circumferential grooves 46 nose 54 of the bearing outer ring 4 can be used as a stop.

It is understood that the arrangement according to the FIGS. 22 to 25 similar to how the other embodiments can be modified in many ways. The number of grooves, the corrugation of the radial corrugated springs or their formation with bumps, the axial and radial guidance and the stops can in each zweckentsprechender way by changing the number of radial corrugated springs, the grooves, additional axial corrugation, the use of O-rings, etc .. . be formed.

FIGS. 26 and 27 show the arrangement of radial corrugated springs 18a between the bearing outer ring 4 and an attached to the bearing outer ring 4 annular sleeve 54 with a total U-shaped cross-section. The radial wave springs 18a are loosely seated on the bearing outer race 4 and held axially by positioning rings 22 disposed between the outer radial wave springs and the radial side walls 56 of the sleeve 54. The sleeve can be produced inexpensively, for example, as sheet metal forming part and fulfilled by appropriately bent formation of the side walls 56 at the same time the function of an axial spring similar to a plate spring. In this way, the storage is according to FIGS. 26 and 27 axially and radially decoupled from the main body 8.

The embodiment according to FIGS. 28 and 29 is different from that of FIGS. 26 and 27 in that, instead of the radial corrugated springs 18a, radial corrugated springs 18b provided with bumps are used, and positioning rings 22 are arranged between the radial corrugated springs 18b.

In the embodiment according to FIGS. 30 to 33 the bearing outer ring 4 is provided with two axially outwardly open circumferential grooves 46 in which axially and radially corrugated radial corrugated springs 18 c are arranged, which are enclosed by a sleeve ring 54. In this embodiment, the sleeve 54 is bent twice in the transition from its bottom to the side walls 56, and serves for axially and radially biased support of the radial wave springs 18c. The sleeve itself has no function of an axial spring. The function of the axial spring or axial decoupling is taken over by the axially corrugated radial corrugated springs 18c. The sleeve 54 serves only as a stop. FIG. 31 shows the enlarged section X of the FIG. 30. FIG. 32 shows a side view of a radial wave spring 18c and FIG. 33 shows a plan view of a section of juxtaposed, and axially corrugated radial corrugated springs 18c.

Based on FIGS. 34 to 45 hereinafter embodiments of decoupling devices will be explained, in which the radial wave springs are formed by an annular spring sleeve.

According to FIG. 34 encloses a cross-sectionally U-shaped annular spring sleeve 18d the bearing outer ring 4 in the axial and radial directions. The bottom of the spring sleeve 18d has a radial corrugation with axial wavelength direction such that an externally visible circumferential groove 58 results. FIG. 35 shows the section X of the FIG. 34 in an enlarged view. It is clearly visible how the outer surface 14 is also formed with a shallow recess, so that the axially formed outside the recess or the groove 58 game d between the inside of the spring sleeve 18 d and the outer surface 14 of the outer ring 4 is smaller than the radial corrugation Spring sleeve 18d. This clearance d is available for a radial displacement of the bearing and can be adjusted by appropriate depth of the recess and height of the corrugation.

Compared with the previously described embodiments, the embodiment is characterized according to FIGS. 34 and 35 by a particularly simple training with few parts. It is understood that the formation of the outer surface 14 of the outer ring 4 with a circumferential recess or groove is not mandatory. With the help of the flat groove in the outer surface 14 of the bearing outer ring 4 is achieved that the curvature of the spring sleeve 18 d can be selected independently of the radial clearance d.

How out FIG. 34 can be seen, the side walls 62 of the spring sleeve 18 d in addition, for example, in the transition region to the bottom 60 outward be curved, so that the spring sleeve takes over the function of an axial spring and radial spring.

The spring sleeve 18d according to FIG. 34 has a radial curvature or undulation with axial wave direction. In contrast, the spring sleeve 18e according to the embodiment FIGS. 36 and 37 a radial corrugation with circumferentially extending wavelength, as shown FIG. 37 can be seen, which is a view in the direction of arrows II-II in FIG. 36 shows. With the embodiment according to FIGS. 36 and 37 the advantage is achieved that larger elastic compliances are achieved by larger possible wavelengths.

The Figures 38 and 39 show a combination of the embodiments of the spring sleeve according to FIGS. 34 to 37 , wherein the spring sleeve 18d of the Figures 38 and 39 having a radial corrugation with axial and circumferentially extending wavelength direction. Thus, an even greater energy absorption capacity due to the elastic deformations in larger material areas of the spring sleeve is achieved.

FIGS. 40 and 41 show an embodiment of a spring sleeve 18g, basically the of FIG. 34 corresponds, but has a plurality of radial bulges with axial wavelength direction, the height of which is different. This allows progressive characteristics to be achieved. With respect to an axial displacement of the bearing, the spring sleeve has 18g no resilient but merely stop action.

The embodiment according to FIGS. 42 and 43 shows a over the entire width of the outer ring 4 extending radial wave spring whose radial corrugation has a wavelength direction in the circumferential direction, the wave heights are different. This makes it possible to achieve more forgiving, progressive identifiers.

It is understood that the radial wave spring 18h can be supplemented by side walls to form a spring sleeve. Further, not only the wave heights but also the wavelengths of the corrugations may be different.

The embodiment according to FIGS. 44 and 45 corresponds to the FIG. 34 , wherein the outer surface of the bearing outer ring 4 is formed without a recess or groove, so that the wave height of the spring ring 18i is equal to the possible radial displacement of the bearing. The side walls of the spring ring 18i extend parallel to the side walls of the bearing outer ring 4, so that the spring sleeve 18i has no function of an axial spring. The spring sleeve 18d of FIG. 45 corresponds to the FIG. 34 , that is, the spring sleeve 18d additionally has the function of an axial spring.

FIG. 46 represents in the left half of the figure in longitudinal section and in the right half of the figure in side view another embodiment of a spring sleeve designed as a radial spring. The bearing outer ring 4 is surrounded by a thin-walled spring steel sheet existing spring sleeve 18j, the is generally U-shaped in cross-section and its radial side walls 66 are radially supported on an annular step 68 which is formed on the side surface of the outer ring 4. A radial compliance is achieved by a crown or radial bulge of the bottom 70 of the spring sleeve 18j. The basic stiffness can be influenced by the sheet thickness. The spring characteristic can be suitably selected by selecting the curvature profile of the floor, optionally multiple corrugated, and / or the contour of the side walls 66. For example, the spring characteristic can be influenced by the fact that the bottom 70 touches the outer surface of the outer ring 4 after a certain radial deformation. Furthermore, an axial compliance of the spring sleeve 18k can be influenced by appropriate design of the side walls 66 and the adjacent side surfaces of the bearing outer ring 4. By asymmetrical bending in its plane, the radial side walls 66 can additionally contribute to the radial compliance of the spring sleeve 18j.

Increased compliance in the circumferential direction can be achieved by radial slots 72 penetrating the bottom 70 and partially the sidewalls 66 of the spring sleeve 18k. Due to the interruption of the membrane stresses in the lateral surface or in the bottom of the spring sleeve 18k and their radial compliance is increased.

Due to the fact that the radial side walls 66 far exceed or surround the outer ring 4, on the one hand the radial space requirement is minimized and on the other hand a relatively large axial compliance is enabled. Slipping off the side walls 66 of the annular step 68 can be prevented if necessary by the formation of the step 68 with a corresponding undercut. The spring sleeve 18j does not have to extend integrally around the entire circumference of the outer ring 4. It can be designed in the form of two circumferential segments. A cohesion of the spring sleeve is ensured in the installed state by the receiving bore or recess of the base body 8, which is facilitated by the crown of the spring sleeve assembly.

For axially fixing the bearing, a circumferential radial projection 74 of the spring sleeve 18j can be used, which engages in an annular groove 76 on the base body 8. The annular groove 76 may be formed by a formed on the inner surface 16 of the base body 8 gradation, which is laterally closed by the attached to the base 8 ring cover 10. It is understood that at low forces to be absorbed, the spring sleeve 18k may be radially formed so resilient that they can be pressed laterally together with the bearing inner ring 2 and the bearing outer ring 4 and the interposed rolling elements 6 in the body, so that the annular groove 76 in the inner surface 16 may be pierced.

The embodiment of the FIG. 47 is different from that of FIG. 46 primarily by the fact that the axial fixation of the spring sleeve 18k is effected by annular surfaces 78 of Einlegeingen 78, via which the spring sleeve 18k is supported on a radial side surface of the base body 8 and the correspondingly formed annular cover 10. The Einlegeringe can for example Plastic exist. An axial constraint of the spring sleeve 18k due to a radial displacement can be avoided if necessary by axial play, but this can be very small.

Figures 48 to 50 illustrate embodiments of the decoupling device that works with radial wave spring segments, the bearing outer ring, not shown 4 ( FIG. 1 ) do not completely enclose, but only along a peripheral region, for example, of about 180 ° and which are arranged on the loaded side of the bearing outer ring.

FIG. 48 shows a side view of a radial wave spring segment 181, which extends over more than half a circumference and is formed with respect to its corrugation similar to, for example, the radial wave spring 18b according to FIG. 4 , To the bearing outer ring, not shown, a plurality of radial wave spring segments 18I are arranged axially adjacent to each other, as in FIG. 49 shown. For positioning the radial wave spring segments 18I in the circumferential direction is a positioning member 82 which is formed as a sleeve segment such that it completely encloses the bearing outer ring 4 together with the radial wave spring segments 181. For fixing in the circumferential direction, the positioning member 82 on axial lugs 84 which engage in recesses which on the main body 8 (FIGS. FIG. 1 ) are formed. In the embodiment according to FIG. 47 is the positioning member 62 formed such that all radial wave spring segments 18I are arranged axially without offset side by side.

In the embodiment according to FIG. 50 the positioning member 82 is provided at its side edges with recesses and projections, so that adjacent radial wave spring segments 18I are each arranged offset in the circumferential direction. This is advantageous for the in FIG. 48 visible support bumps 24 and bumps 26 (for more details see FIG. 4 ) are arranged, for example, on a gap.

An advantage associated with the embodiments according to Figures 48 to 50 is achieved, is that the utilization of, for example, complex blanking plate for the radial wave springs with respect to the formation of radial corrugated springs, which extend over the entire circumference (possibly with slot), is significantly improved.

The claims filed with the application are formulation proposals without prejudice to the achievement of further patent protection. The Applicant reserves the right to claim further, previously only disclosed in the description and / or drawings feature combination.

Relationships used in subclaims indicate the further development of the subject of the main claim by the features of the respective subclaim; they should not be construed as a waiver of the attainment of independent, objective protection for the feature combinations of the dependent claims.

Since the subject-matter of the subclaims can form separate and independent inventions with regard to the prior art on the priority date, the Applicant reserves the right to make them the subject of independent claims or statements of division. They may further contain independent inventions having an independent of the subjects of the preceding sub-claims design.

The embodiments are not to be understood as limiting the invention. Rather, numerous modifications and variations are possible within the scope of the present disclosure, in particular those variants, elements and combinations and / or materials, for example, by combination or modification of individual in conjunction with those described in the general description and embodiments and the claims and in The features or elements or method steps contained in the drawings for the expert with regard to the solution of the problem can be removed and lead by combinable features to a new subject or to new process steps or process steps, even if they concern manufacturing, testing and working procedures.

Claims (14)

1. Decoupling device for a bearing arrangement of a shaft on a basic body (8), in particular of a shaft of a continuously variable cone-pulley transmission which operates with a chain as an endless chain-belt, comprising

   - a bearing outer ring (4) which is formed with a cylindrical outer surface (14) and within which the shaft is mounted, and

   - an inner surface (16) which is rigidly connected to the basic body (8) and which surrounds the outer surface (14),
   wherein at least one radial ondular washer (18d - 18k) is arranged between the outer surface (14) and the inner surface (16), which radial ondular washer, under elastic deformation, permits a limited relative radial movement between the inner surface (16) and the outer surface (14), characterized in that a spring sleeve which forms the radial ondular washer (18d - 18k) and which has a U-shaped overall cross section is placed onto the outer surface (14) and onto side surfaces which run radially relative to said outer surface, the base (60) of which spring sleeve runs axially parallel overall and is radially bulged.
2. Decoupling device according to Claim 1, wherein the base (60) has at least two axially spaced apart encircling radial undulations with an axial wavelength direction.
3. Decoupling device according to Claim 1 or 2, wherein an annular region (58) between the radial undulations projects into an encircling recess of the outer surface (14).
4. Decoupling device according to one of Claims 1 to 3, wherein the base (60) of the spring sleeve (18e) has a radial undulation with a wavelength direction running in the circumferential direction.
5. Decoupling device according to Claim 1, wherein radial undulations of the base (60) with a wavelength direction running in the axial and/or in the circumferential direction have different heights.
6. Decoupling device according to one of Claims 1 to 5, wherein radial side surfaces of the outer surface (14) are supported in an elastically flexible manner in the axial direction against radial side surfaces of the inner surface (16) via the curved side walls (62), which run radially overall, of the spring sleeve (18d).
7. Decoupling device according to Claim 1, wherein the radial side walls (66) of the spring sleeve (18j; 18k) are supported radially on an annular step (68) of radial side surfaces of the outer surface (14), and the base (70), which bears against the inner surface (16), of the spring sleeve (18j; 18k) is of convex design.
8. Decoupling device according to Claim 7, wherein the spring sleeve (18j; 18k) is formed with radial slots (72) which cut through the base (70).
9. Decoupling device according to Claim 7 or 8, wherein an encircling projection (74) of the base (70) engages into an annular groove (76) of the inner surface (16).
10. Decoupling device according to Claim 7 or 8, wherein, on at least one radially inwardly running side surface which axially delimits the inner surface (16), there is formed an annular surface (78) against which the spring sleeve is axially supported.
11. Decoupling device according to one of Claims 7 to 9, wherein the side walls (66) of the spring sleeve (18; 18k) are of axially and/or radially elastically flexible design.
12. Decoupling device according to one of Claims 1 to 11, wherein the radial ondular washer is formed by spring segments which extend over parts of the circumference of the inner surface or the outer surface.
13. Radial ondular washer for a decoupling device according to one of the preceding claims for surrounding at least a part of the circumference of a bearing ring (4) which is formed with a round cylindrical outer surface and with radial side surfaces adjoining said outer surface, characterized in that the radial ondular washer is formed as a spring sleeve (18d - 18k) which surrounds at least one circumferential segment of the bearing ring and which has a U-shaped overall cross section, wherein at least the base (60; 70)
    of the spring sleeve has a resiliently deformable bulge.
14. Radial ondular washer according to Claim 13, wherein the base (70) is formed with a radial projection (74) running in the circumferential direction.

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